EP0465080B1 - Selbstverstärkende Synchronisiereinrichtung - Google Patents

Selbstverstärkende Synchronisiereinrichtung Download PDF

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Publication number
EP0465080B1
EP0465080B1 EP91305705A EP91305705A EP0465080B1 EP 0465080 B1 EP0465080 B1 EP 0465080B1 EP 91305705 A EP91305705 A EP 91305705A EP 91305705 A EP91305705 A EP 91305705A EP 0465080 B1 EP0465080 B1 EP 0465080B1
Authority
EP
European Patent Office
Prior art keywords
sprag
synchronizing
clutch
members
synchronization
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP91305705A
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English (en)
French (fr)
Other versions
EP0465080A2 (de
EP0465080A3 (en
Inventor
John Roland Vandervoort
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Eaton Corp
Original Assignee
Eaton Corp
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Filing date
Publication date
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Publication of EP0465080A2 publication Critical patent/EP0465080A2/de
Publication of EP0465080A3 publication Critical patent/EP0465080A3/en
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Publication of EP0465080B1 publication Critical patent/EP0465080B1/de
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Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/02—Arrangements for synchronisation, also for power-operated clutches
    • F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
    • F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
    • F16D23/0606—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation the blocking mechanism comprising an axially-extending shouldered pin passing through a hole in a radial wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/069—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by pivoting or rocking, e.g. sprags
    • F16D41/07—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by pivoting or rocking, e.g. sprags between two cylindrical surfaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/02—Arrangements for synchronisation, also for power-operated clutches
    • F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
    • F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
    • F16D2023/065—Means to provide additional axial force for self-energising, e.g. by using torque from the friction clutch
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19219—Interchangeably locked
    • Y10T74/19284—Meshing assisters

Definitions

  • the present invention relates to ring and pin type cone synchronizers employed for matching the speed of rotation of drive elements employed in a power transmission and particularly relates to changeable ratio power transmissions employed in vehicle drive trains.
  • the synchronizer of the present invention is particularly applicable to heavy duty transmissions for trucks and off-highway vehicles where the axial force required to activate synchronization of the power elements to be engaged, is relatively high. This condition arises particularly in heavy duty truck transmissions where the cone angle of the annular tapered synchronizing surface is a relatively small angle and a substantial wedging effect is created due to the low cone angle of the synchronizing surfaces.
  • US-A-1 952 461 proposes the use of sprag members, in a synchronizer, either from one or from both senses of overrun. A more effective use of sprags for synchronization was found desirable.
  • DE-A-1 775 192 proposes synchronization using intermediate spherical rolling members to effect a wedging action with inclined surfaces cut into a clutch means and rings associated with drive gear means, and represents the state of the art, defining the pre-characterizing portion of Claim 1.
  • the present invention can provide a ring and pin cone type synchronizer having self-energizing action for use in providing synchronization of drive elements during ratio changes in a power transmission.
  • the present invention utilizes a synchronizer ring for frictionally engaging a relatively low angle cone synchronizing surface on a drive member to be engaged and employs axially extending pins thereabout for engaging a sliding clutch member for providing the axial force on the synchronizer ring to effect frictional speed synchronization of the relatively rotatable power driving elements prior to positive driving engagement with the clutch member.
  • the synchronizer ring of the present invention as embodied, can have a plurality of sprag members pivotally mounted thereon in circumferentially spaced engagement.
  • Each of the sprag members has the one outer surface thereof axially tapered to match the taper of the friction cone surface on the drive member.
  • the sprag members are each pivotable on the ring such that upon axial movement of the ring frictional engagement of the sprag members occurs when contacting the friction cone surface.
  • the sprag members are pivoted by the tangential frictional forces of the cone acting thereon to be cammed on the synchronizer ring, for thereby increasing the frictional forces.
  • the sprag members Upon overrunning of the other of the said power driver elements with respect to the said one element, the sprag members are pivoted to prevent such camming action and permit slippage to occur, thus unlocking the synchronization.
  • the pivoting of the sprag members for the camming action thus provides a self-energizing action to the synchronizing ring.
  • the state of the art requires angular cut-outs from facing surfaces, and these face axially.
  • Preferred embodiments of the present invention have the intermediate rolling sprag members between radially spaced surfaces, one being conical.
  • the present invention thus provides a self-energizing synchronizer employing pivotal sprag members on the synchronizer ring for facilitating synchronization and release thereof upon reaching synchronization.
  • the use of sprag members to effect synchronization as aforesaid is proposed in US-A-1 952 461, but requires one spring for each sprag and arcuate depressions, thus restricting the rolling or pivotting of the sprag member.
  • the sprags are symmetric to effect camming in either case of overrunning to give self-energizing both conditions, i.e., when one drive element overruns the other.
  • the synchronizing assembly of the present invention is indicated generally at 10 and is typically employed in a heavy duty transmission for a vehicle power train wherein an input shaft 12 has drivingly attached thereto an input gear 14 having the outer periphery thereof provided with a plurality of teeth 16 which are adapted for drivingly engaging countershaft gear 18, indicated in dashed outline in Figure 1, for driving a countershaft 20, indicated in dashed outline, which has attached thereto a second countershaft gear 22 also indicated in dashed outline.
  • Input gear 14 also has on the free axial end thereof adjacent the end of shaft 12 a counterbore 24 having disposed about the circumference thereof a plurality of spaced radially inwardly extending lugs or teeth 28. Input gear 14 also has disposed on the outer periphery thereof and axially adjacent the teeth 16 a conically tapered surface 30 adapted for frictional engagement therewith. It will be understood that shaft 12 is suitably journalled on the gear case or housing (not shown) in a manner well known in the art.
  • An output shaft or mainshaft 32 is disposed axially coincident and spaced from shaft 12; and, is suitably journalled for rotation on the gear casing or housing (not shown) as for example by a tapered roller bearing having a plurality of rollers 34 adapted for engaging an outer race (not shown) provided on the housing.
  • Shaft 32 has an output gear 36 received concentrically thereover and having a plurality of teeth 38 provided about the outer periphery thereof adapted for receiving power from the countershaft gear 22.
  • Output gear 36 is journalled for rotation in a bearing race 40 attached to the surface of shaft 32 by means of a radially inwardly extending flange 44 provided on gear 36 which secures the gear in the desired axial location on the shaft 32.
  • An annular dog clutch member 46 is slidably received over the shaft 32 and engages the shaft by means of a plurality of splines 48 disposed about the circumference of the shaft 32 and which are engaged by complementary splines 50 provided on the inner periphery of the dog clutch 46.
  • the clutch 46 has a first row of circumferentially spaced dogs or teeth 52 provided at one axial end thereof. Upon sliding movement of the clutch 46, from the position shown in solid outline in Figure 1 leftward to the position shown in dashed outline, the teeth 52 engage the dogs or teeth 28 provided on the input gear 14 for power transmission therebetween.
  • the clutch 46 has a second row of circumferentially spaced dogs or teeth 54 provided thereon and disposed at the axial end opposite dogs 52 and which, in the position shown in solid outline in Figure 1, engage a complementary set of circumferentially spaced internal teeth 56 provided about output gear 36. It will be understood that with clutch member 46 in the position shown in solid outline in Figure 1 that power is transmitted from input gear 14 through countershaft gear 18 shaft 20 and countershaft gear 22 to output gear 36 which is drivingly engaged to the shaft 32 by virtue of engagement of the dogs or teeth 54,56.
  • Clutch member 46 has a circumferental groove 58 provided about the outer periphery thereof which is adapted for receiving therein a clutch fork (not shown) for effecting user selected axial movement of the member 46 between the position shown in the solid and dashed outlines in Figure 1 as is well known in the art.
  • a first annular synchronizing ring 60 is provided concentrically over the friction cone surface 30.
  • the ring 60 has a circumferential groove 62 provided about the inner periphery thereof.
  • a plurality, preferably three, circumferentially spaced pins are provided about the axial face of ring 60 one of which is illustrated and denoted generally by reference numeral 64 in Figure 1.
  • Each of the pins 64 has a reduced diameter or pilot portion 66 which extends through a corresponding substantially larger diameter aperture 68 provided in the clutch member 46.
  • the root portion of each of the pins 64 is formed to a larger diameter 70 which is a close sliding fit with the aperture 68 when the clutch 46 is moved fully to the engaged position shown in dashed outline in Figure 1.
  • synchronizer ring 60 has a plurality of pivotally movable sprag members 72 disposed in circumferentially spaced arrangement about the groove 62 and retained in such spaced arrangement by an annular cage ring or spacer element 74, with each sprag 72 received through an aperture 76 provided in the cage.
  • the radially inner surface of each of the sprags of Figure 2 is tapered at an angle corresponding to the cone angle of surface 30.
  • the sprag members are pivoted in a clockwise direction about the aperture 76 upon axial movement of the ring 60 to bring the surfaces 78 in contact with friction cone 30; and, a camming action of the sprag members does not occur because of the configuration of the radially inner and radially outer ends of the sprag member 72 as shown in Figure 2. Therefore, the arrangement of the sprag members of the embodiment of Figure 2 is considered to be a "one way" synchronizer.
  • a second annular synchronizer ring 80 is provided and is received in an annular groove 82 provided in the axial face of gear 36.
  • the outer periphery of groove 82 has a conical friction surface 84 formed thereon.
  • the second synchronizer ring 80 is nested in groove 82 in free sliding arrangement and has a plurality, preferably three, of pins indicated generally at 86 spaced circumferentially thereabout and extending axially from the lefthand axial face of ring 80 as illustrated in Figure 1.
  • Each of the three pins 86 has a lesser diameter portion 88 at the outer end thereof; and, the root portion 90 is formed of a larger diameter which can enter a corresponding aperture 92 provided in clutch 46 in free sliding engagement.
  • Each of the pins 86 has a chamfered step 89 intermediate the diameters 88,90.
  • synchronizer ring 80 has a circumferential groove 99 formed in the outer periphery thereof.
  • the groove 99 has received therein a plurality of two-way sprag members 88 disposed in circumferentially spaced arrangement in the groove 99 and spaced therein by suitable cage ring 91 having apertures 92 formed therein with the edges of the aperture 92 providing pivot surfaces for the sprag member 88.
  • the groove 99 has the radially inner wall thereof formed as generally a right cylindrical surface 94 with the radially inner surface 96 of the sprag member curved to a smaller radius than the radially outer surface 98 of the sprag member.
  • the present invention thus provides a unique and novel synchronizing assembly for facilitating gear ratio changes in a power transmission and employs a plurality of circumferentially spaced pivotally movable sprag members disposed about the synchronizer ring for providing a positive camming action between the synchronizer ring and the friction cone surface on the power transmission element to be synchronized.
  • the sprag members of the present invention provide increased tangential frictional forces with minimum axial force to facilitate synchronization and to thereby prevent wedging of the synchronizer ring and the friction cone for low angle friction cones.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Structure Of Transmissions (AREA)

Claims (9)

  1. Veränderbares Verhältnisleistungsgetriebe, das folgendes aufweist:
    eine selbsterregende bzw. selbstverstärkende Synchronisiervorrichtung zum Erleichtern des Ineingriffkommens von Zahnrädern (14, 16) mit einer Welle (12, 32);
    (a) wobei die Welle eine Drehmomentübertragungswelle (12, 32) ist mit Verschiebungskupplungsmitteln (46), die axial bezüglich zur der Welle bewegbar sind, zwischen einer Eingriffs- und einer Nicht-Eingriffsposition, wobei die Kupplungsmittel axial in Eingriff bringbare Antriebszahnmitteln (52, 54) daran aufweisen und wobei die Kupplungsmittel mit einer der Wellen (32) zur Drehung damit gekuppelt sind;
    (b) wobei die Zahnräder Antriebszahnradmittel (14, 36) sind, die zur konzentrischen Drehung bezüglich der Wellenmittel (12, 32) (drehbar) gelagert sind und eine konische Synchronisierreibungsoberfläche (30, 84) besitzen, die damit assoziiert ist, wobei die Antriebszahnradmittel Zahnmittel (28, 56) daran besitzen, die axial in Eingriff bringbar mit den Kupplungszahnmitteln (52, 54) sind;
    (c) Synchronisierringmittel (60, 80), die durch die Kupplungsmittel (46) gedrückt werden und beim Anlegen einer axialen Verschiebungskraft darauf axial bewegbar sind zum reibungsmäßigen Kontaktieren der konischen Oberfläche (30, 84) und zum Bewirken einer Drehgeschwindigkeit bzw. Drehzahlsynchronisierung zwischen den Kupplungsmitteln (46) und den Zahnradmitteln (14, 36), um dadurch eine Bewegung der Kupplungsmittel in die Eingriffsposition zu erlauben, wobei die Ringmittel (60, 80) und die Zahnradmittel damit assoziiert ein zwischenliegendes rollbares Glied (72, 78) besitzen, das relativ zu den Ringmitteln rollbar ist zum Bewirken einer selbstverstärkenden bzw. selbsterregenden Synchronisierung;
    dadurch gekennzeichnet, daß
    die konische Reibungsoberfläche (30, 84) mit den Antriebszahnradmitteln (14, 36) assoziiert ist; daß die Zahnradmittel (14, 36) auch mit dem Zwischenglied (72, 88) assoziiert sind, von denen es eine Vielzahl gibt; wobei die Zwischenglieder Verbindungs- oder Hemmschuhglieder (72, 88) sind und an den Ringmitteln (60,88) schwenkbar bewegbar sind; daß bei einer Axialbewegung der Ringmittel die Hemmschuhglieder (72, 88) einen Reibungskontakt mit der konischen Oberfläche (30, 84) an den Zahnradmitteln (14, 36) herstellen, und die Tangentialkräfte des Reibungskontakts eine Schwenkbewegung der Hemmschuhglieder in einer Richtung bewirken, die die Reibungskräfte erhöhen zum Bewirken der selbstverstärkenden bzw. selbsterregenden Synchronisierung, und zwar so lange, wie ein wesentliche Drehzahldifferenz in mindestens einer Richtung und die axiale Verschiebungskraft beibehalten werden und daß bei einer Synchronisierung und beim Lösen der axialen Verschiebungskraft die Hemmschuhglieder (72, 88) in eine gelöste Position schwenkbar sind.
  2. Getriebe nach Anspruch 1, wobei jedes der Hemmschuhmittel (78) so aufgebaut ist, daß die selbstverstärkende Schwenkbewegung nur auftritt, wenn die Zahnradmittel (14) schneller laufen wie die Wellenmittel (12).
  3. Getriebe nach Anspruch 1, wobei jedes der Hemmschuhmittel (88) so aufgebaut ist, daß die selbstverstärkende Schwenkbewegung auftritt, wenn entweder eines der Zahnradmittel (36) oder der Wellenmittel (32) schneller läuft wie die anderen Mittel.
  4. Getriebe nach Anspruch 1, wobei jede Außenoberfläche (98) der Hemmschuhglieder (88) konisch verjüngt ist, und zwar komplementär zu der konischen Synchronisieroberfläche (84) und wobei der Mittelbereich der äußeren verjüngten Oberfläche und der radial inneren Oberfläche (96) der Hemmschuhglieder (88) jeweils gekrümmt ist, und zwar mit einem ersten Radius und deren Ränder mit einem zweiten Radius gekrümmt sind, der größer ist wie der erste Radius.
  5. Getriebe nach Anspruch 1, wobei die Ringmittel (80) eine im allgemeinen zylindrische Oberfläche (94) definieren, die zum Nocken bzw. Hubkontakt mit der radial inneren Oberfläche (96) jedes Hemmschuhgliedes angeordnet ist.
  6. Getriebe nach Anspruch 1, gekennzeichnet durch:
    (a) erste ringförmige Synchronisiermittel (60), die Mittel (72, 78) aufweisen, die Reibungsoberflächen definieren, die komplementär sind zu den ringförmig verjüngten Oberflächen (30) der Eingangswellenmittel, wobei das erste Synchronisierglied Oberflächen (100) daran definiert, die mit den Kupplungsmitteleingiffsoberflächen (67) in Eingriff kommen, und zwar in einer tangentialen Richtung und eine axiale Gleitbewegung dazwischen erlauben, wobei die Mittel, die die Reibungsoberflächen definieren, eine Vielzahl von umfangsmäßig beabstandeten Hemmschuhgliedern (72) aufweisen, die schwenkbar bewegbar sind zum Bewirken einer reibungsmäßigen Synchronisierung des ringförmigen Gliedes mit der ringförmigen verjüngen Oberfläche (30) der Eingangswellenmittel an einer der Eingangswellenmittel (14) und wobei die Synchronisiermittel (60) schneller laufen als die anderen, und betriebsmäßig das Lösen der reibungsmäßigen Synchronisierung bewirken, wenn die anderen schneller laufen wie die eine, wobei die Kupplungsmittel (46) betätigbar sind auf die Bewegung eines Bedieners aus einer ersten zu einer zweiten Axialposition, um Sychronisierung und Eingriff der Kupplungsmittel (46) und der Eingangszahnradmittel (12) zu bewirken; und durch
    (b) zweite ringförmige Synchronisiermittel (80), die Mittel aufweisen, die Reibungsoberflächen definieren, die komplementär sind zu der ringförmig verjüngte Oberfläche (84) der Ausgangszahnradmittel und eine Vielzahl von umfangsmäßig beabstandeten Hemmschuhgliedern (88) aufweisen, die schwenkbar bewegbar sind, um eine selbstverstärkende Reibungssynchronisierung der zweiten Synchronisiermittel mit den Ausgangszahnradmitteln zu bewirken, und zwar auf eine Axialbewegung der zweiten Synchronisiermittel durch den Bediener hin, wenn die Ausgangswellenmittel schneller laufen als die Ausgangszahnradmittel, wobei die Hemmschuhglieder (88) schwenkbar bewegbar sind, um die Reibungsynchronisierung zu lösen, wenn die Ausgangsszahnradmittel schneller laufen als die Ausgangswellenmittel.
  7. Getriebe nach Anspruch 6, dadurch gekennzeichnet, daß, wenn die Hemmschuhglieder (72) der Ausgangswelle und der Ringmittel in einer gegebenen Drehrichtung schneller laufen wie die Ausgangszahnradmittel sie sich betriebsmäßig schwenken und reibungsmäßig mit der konischen Synchronisieroberfläche und der ringförmigen Oberfläche in Eingriff kommen, um eine Relativdrehung des Ausgangszahnrades bezüglich der Ringmittel zu verhindern und wenn das Ausgangszahnrad (14) schneller läuft wie die Ausgangswelle (12), daß die Hemmschuhglieder (72) schwenkbar bewegt werden, um einen Schlupf oder ein Verrutschen zu erlauben.
  8. Getriebe nach Anspruch 7, wobei jedes der Hemmschuhglieder, dessen radial äußere Oberfläche mit einer Verjüngung konfiguriert besitzt, die komplementär ist zu der konischen Synchronisieroberfläche.
  9. Getriebe nach Anspruch 7, wobei jedes der Hemmschuhglieder dessen radial innere Oberfläche davon konfiguriert besitzt, und zwar komplementär zu der ringförmigen Reibungsoberfläche.
EP91305705A 1990-07-02 1991-06-24 Selbstverstärkende Synchronisiereinrichtung Expired - Lifetime EP0465080B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US548354 1990-07-02
US07/548,354 US5069079A (en) 1990-07-02 1990-07-02 Self-energizing synchronizer

Publications (3)

Publication Number Publication Date
EP0465080A2 EP0465080A2 (de) 1992-01-08
EP0465080A3 EP0465080A3 (en) 1992-06-03
EP0465080B1 true EP0465080B1 (de) 1995-05-10

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EP91305705A Expired - Lifetime EP0465080B1 (de) 1990-07-02 1991-06-24 Selbstverstärkende Synchronisiereinrichtung

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Country Link
US (1) US5069079A (de)
EP (1) EP0465080B1 (de)
JP (1) JP3092019B2 (de)
CA (1) CA2045874C (de)
DE (1) DE69109550T2 (de)
ES (1) ES2071921T3 (de)

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US4373620A (en) * 1979-10-26 1983-02-15 Dana Corporation Elastomeric energizer for sprag clutch
US4756395A (en) * 1985-12-03 1988-07-12 Dana Corporation Overrunning clutch with controlled sprag action
US5052533A (en) * 1987-02-09 1991-10-01 Borg-Warner Corporation One-way clutch energizing spring
US4796741A (en) * 1987-12-11 1989-01-10 Dana Corporation Synchronizer blocker pin mounting structure

Also Published As

Publication number Publication date
CA2045874A1 (en) 1992-01-03
CA2045874C (en) 1995-02-21
JPH04231726A (ja) 1992-08-20
EP0465080A2 (de) 1992-01-08
DE69109550D1 (de) 1995-06-14
JP3092019B2 (ja) 2000-09-25
EP0465080A3 (en) 1992-06-03
US5069079A (en) 1991-12-03
DE69109550T2 (de) 1996-02-08
ES2071921T3 (es) 1995-07-01

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